CN106870654B

CN106870654B - Planetary gear train of automatic transmission for vehicle

Info

Publication number: CN106870654B
Application number: CN201610878553.6A
Authority: CN
Inventors: 池晟旭; 黄圣旭; 权贤植; 赵源珉; 鞠再昌
Original assignee: Hyundai Motor Co
Current assignee: Hyundai Motor Co
Priority date: 2015-12-02
Filing date: 2016-10-08
Publication date: 2021-03-23
Anticipated expiration: 2036-10-08
Also published as: US20170159771A1; KR20170064939A; US9822855B2; KR101786694B1; CN106870654A

Abstract

A planetary gear train of an automatic transmission for a vehicle, may include: an input shaft for receiving torque of an engine; an output shaft for outputting the changed torque; a first planetary gear set; a second planetary gear set; a third planetary gear set; a fourth planetary gear set; six control elements; a first shaft selectively connectable with the transmission housing; a second shaft; a third axis; a fourth shaft directly connected with the input shaft; a fifth shaft selectively connectable with the third shaft and selectively connectable with the transmission housing; a sixth shaft selectively connectable with at least one of the first shaft and the fourth shaft; a seventh shaft directly connected with the output shaft; and an eighth shaft selectively connectable with the sixth shaft.

Description

Planetary gear train of automatic transmission for vehicle

Cross Reference to Related Applications

This application claims priority from korean patent application No. 10-2015-0170991, filed on 2.12.2015, the entire contents of which are incorporated herein for all purposes by this reference.

Technical Field

The present invention relates to an automatic transmission for a vehicle. More particularly, the present invention relates to a planetary gear train of an automatic transmission for a vehicle, which includes: which improves power transmission performance and fuel efficiency by achieving ten forward speed ranges using a drive point set at a low engine speed.

Background

Recently, the rise in oil prices has caused a strong competition for improving fuel consumption of vehicles.

Under such circumstances, research has been conducted on engines to reduce weight and improve fuel efficiency by downsizing, and research has also been conducted on maximizing fuel efficiency by realizing automatic transmissions having a plurality of speed ranges while ensuring drivability and competitiveness.

However, in the automatic transmission, as the number of speed gears increases, the number of internal members (particularly, planetary gear sets) thereof also increases, which deteriorates the mountability and/or power flow efficiency, and increases the production cost and weight.

Therefore, in order to increase the effect of improving fuel efficiency by implementing an automatic transmission having a plurality of speed stages, it is important to develop a planetary gear train capable of maximizing efficiency with a small number of components.

In this regard, an eight-speed automatic transmission has recently been introduced, and a planetary gear train for an automatic transmission capable of achieving more gears is also under development.

The information disclosed in this background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.

Disclosure of Invention

Various aspects of the present invention are directed to provide a planetary gear train of an automatic transmission for a vehicle, which has advantages in that: the power transmission performance and fuel cost are improved by multi-shifting gears by realizing ten forward speed gears and one reverse gear with the simplest configuration; and improves the quiet driveability of the vehicle by using a driving point in a low Revolution Per Minute (RPM) range of the engine.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include: an input shaft for receiving torque of an engine; an output shaft for outputting the changed torque; a first planetary gear set including a first rotating element, a second rotating element, and a third rotating element; a second planetary gear set including a fourth rotating element, a fifth rotating element and a sixth rotating element; a third planetary gear set including a seventh rotary element, an eighth rotary element, and a ninth rotary element; a fourth planetary gear set including a tenth rotating element, an eleventh rotating element, and a twelfth rotating element; six control elements for selectively interconnecting the rotary elements or selectively interconnecting the rotary elements with the transmission housing; a first shaft integrally connected with the first rotating element and selectively connectable with a transmission housing; a second shaft integrally connected with the second rotating element and integrally connected with the sixth rotating element; a third shaft integrally connected with the third rotating element and integrally connected with the seventh rotating element; a fourth shaft integrally connected with the fourth rotating element, integrally connected with the twelfth rotating element, and directly connected with the input shaft; a fifth shaft integrally connected with the fifth rotating element and selectively connectable with the third shaft and selectively connectable with the transmission housing; a sixth shaft integrally connected with the eighth rotating element and selectively connectable with at least one of the first shaft and the fourth shaft; a seventh shaft integrally connected with the ninth rotating element, integrally connected with the eleventh rotating element, and directly connected with the output shaft; and an eighth shaft integrally connected with the tenth rotating element and selectively connectable with the sixth shaft.

The first planetary gear set may be a single pinion planetary gear set, wherein the first rotating element may be a first sun gear, the second rotating element may be a first planet carrier, and the third rotating element may be a first ring gear; the second planetary gear set may be a single pinion planetary gear set, wherein the fourth rotating element may be a second sun gear, the fifth rotating element may be a second planet carrier, and the sixth rotating element may be a second ring gear; the third planetary gear set may be a single pinion planetary gear set, wherein the seventh rotating element may be a third sun gear, the eighth rotating element may be a third planet carrier, and the ninth rotating element may be a third ring gear; and the fourth planetary gear set may be a single pinion planetary gear set, wherein the tenth rotating element may be a fourth sun gear, the eleventh rotating element may be a fourth planet carrier, and the twelfth rotating element may be a fourth ring gear.

The six control elements may include: a first clutch selectively connecting the fourth shaft and the sixth shaft; a second clutch selectively connecting the sixth shaft and the eighth shaft; a third clutch selectively connecting the third shaft and the fifth shaft; a fourth clutch selectively connecting the first shaft and the sixth shaft; a first brake selectively connecting the fifth shaft and the transmission housing; and a second brake selectively connecting the first shaft and the transmission housing.

The gears achieved by selective operation of three of the six control elements include: a first forward speed stage formed by operations of the fourth clutch, the first brake, and the second brake; a second forward speed stage formed by operations of the second clutch, the fourth clutch, and the second brake; a third forward speed stage formed by operations of the second clutch, the fourth clutch, and the first brake; a fourth forward speed stage formed by operations of the second clutch, the third clutch, and the first brake; a fifth forward speed stage formed by operations of the second clutch, the third clutch, and the second brake; a sixth forward speed stage formed by operations of the first clutch, the second clutch, and the third clutch; a seventh forward speed stage formed by operations of the first clutch, the third clutch, and the second brake; an eighth forward speed stage formed by operations of the first clutch, the third clutch, and the first brake; a ninth forward speed stage formed by operations of the first clutch, the first brake, and the second brake; a tenth forward speed stage formed by operations of the first clutch, the fourth clutch, and the first brake; and a reverse gear formed by operations of the third clutch, the fourth clutch, and the second brake.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include: an input shaft for receiving torque of an engine; an output shaft for outputting the changed torque; a first planetary gear set that is a single pinion planetary gear set and includes a first rotating element, a second rotating element, and a third rotating element; a second planetary gear set that is a single pinion planetary gear set and includes a fourth rotating element, a fifth rotating element, and a sixth rotating element; a third planetary gear set that is a single pinion planetary gear set and includes a seventh rotary element, an eighth rotary element, and a ninth rotary element; a fourth planetary gear set that is a single pinion planetary gear set and includes a tenth rotating element, an eleventh rotating element, and a twelfth rotating element; a first shaft integrally connected with the first rotating element and selectively connectable with a transmission housing; a second shaft integrally connected with the second rotating element and integrally connected with the sixth rotating element; a third shaft integrally connected with the third rotating element and integrally connected with the seventh rotating element; a fourth shaft integrally connected with the fourth rotating element, integrally connected with the twelfth rotating element, and directly connected with the input shaft; a fifth shaft integrally connected with the fifth rotating element and selectively connectable with the third shaft and selectively connectable with the transmission housing; a sixth shaft integrally connected with the eighth rotating element and selectively connectable with at least one of the first shaft and the fourth shaft; a seventh shaft integrally connected with the ninth rotating element, integrally connected with the eleventh rotating element, and directly connected with the output shaft; an eighth shaft integrally connected with the tenth rotating element and selectively connectable with the sixth shaft; a first clutch selectively connecting the fourth shaft and the sixth shaft; a second clutch selectively connecting the sixth shaft and the eighth shaft; a third clutch selectively connecting the third shaft and the fifth shaft; a fourth clutch selectively connecting the first shaft and the sixth shaft; a first brake selectively connecting the fifth shaft and the transmission housing; and a second brake selectively connecting the first shaft and the transmission housing.

The first planetary gear set may include: a first sun gear as a first rotating element, a first planet carrier as a second rotating element, and a first ring gear as a third rotating element; the second planetary gear set may include: a second sun gear as a fourth rotating element, a second carrier as a fifth rotating element, and a second ring gear as a sixth rotating element; the third planetary gear set may include: a third sun gear as a seventh rotating element, a third carrier as an eighth rotating element, and a third ring gear as a ninth rotating element; and the fourth planetary gear set may include: a fourth sun gear as a tenth rotating element, a fourth carrier as an eleventh rotating element, and a fourth ring gear as a twelfth rotating element.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include: an input shaft for receiving torque of an engine; an output shaft for outputting the changed torque; a first planetary gear set as a single pinion planetary gear set and including a first sun gear, a first planet carrier, and a first ring gear; a second planetary gear set which is a single pinion planetary gear set and includes a second sun gear, a second carrier, and a second ring gear; a third planetary gear set as a single pinion planetary gear set and including a third sun gear, a third planet carrier, and a third ring gear; a fourth planetary gear set which is a single pinion planetary gear set and includes a fourth sun gear, a fourth planet carrier, and a fourth ring gear; a first shaft integrally connected with the first rotating element and selectively connectable with a transmission housing; a second shaft integrally connected with the second rotating element and integrally connected with the sixth rotating element; a third shaft integrally connected with the third rotating element and integrally connected with the seventh rotating element; a fourth shaft integrally connected with the fourth rotating element, integrally connected with the twelfth rotating element, and directly connected with the input shaft; a fifth shaft integrally connected with the fifth rotating element and selectively connectable with the third shaft and selectively connectable with the transmission housing; a sixth shaft integrally connected with the eighth rotating element and selectively connectable with at least one of the first shaft and the fourth shaft; a seventh shaft integrally connected with the ninth rotating element, integrally connected with the eleventh rotating element, and directly connected with the output shaft; an eighth shaft integrally connected with the tenth rotating element and selectively connectable with the sixth shaft; and six control elements for selectively interconnecting the shafts or selectively interconnecting the shafts with the transmission housing.

It should be understood that the term "vehicle" or "vehicular" or other similar terms as used herein generally includes motor vehicles such as passenger automobiles including Sport Utility Vehicles (SUVs), buses, trucks, various commercial vehicles, watercraft including a variety of boats, ships, aircraft, and the like, and includes hybrid vehicles, electric vehicles, plug-in hybrid electric vehicles, hydrogen-powered vehicles, and other alternative fuel vehicles (e.g., fuels derived from non-petroleum sources). As referred to herein, a hybrid vehicle is a vehicle having two or more power sources, such as both gasoline-powered and electric-powered vehicles.

The method and apparatus of the present invention have other features and advantages which will be apparent from or are set forth in detail in the accompanying drawings and the following embodiments incorporated herein, which together serve to explain certain principles of the invention.

Drawings

FIG. 1 is a schematic diagram of a planetary gear train according to various embodiments of the present invention;

fig. 2 is an operation diagram of respective control elements in respective gears in a planetary gear train according to various embodiments of the present invention.

It is to be understood that the drawings are not necessarily to scale, presenting a simplified representation of various features illustrative of the invention, illustrative of the basic principles of the invention. The specific design features disclosed herein, including, for example, specific dimensions, orientations, locations, and shapes, will be determined in part by the particular application and environment in which it is used.

Detailed Description

Reference will now be made in detail to various embodiments of the invention, examples of which are illustrated in the accompanying drawings and described below. While the invention will be described in conjunction with the exemplary embodiments, it will be understood that this description is not intended to limit the invention to these exemplary embodiments. On the contrary, the invention is intended to cover not only these exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the invention as defined by the appended claims.

FIG. 1 is a schematic diagram of a planetary gear train according to various embodiments of the present invention.

Referring to fig. 1, a planetary gear train according to various embodiments of the present invention includes: a first planetary gear set PG1, a second planetary gear set PG2, a third planetary gear set PG3, and a fourth planetary gear set PG4 disposed on the same axis; an input shaft IS; an output shaft OS; eight rotation shafts TM1 to TM 8; six control elements C1-C4 and B1-B2; and a transmission case H that directly connects the rotary elements of the first, second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4 with each other by eight rotary shafts TM1 to TM 8.

The torque input from the input shaft IS changed by the cooperative work of the first, second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4, and then output via the output shaft OS.

These simple planetary gear sets are arranged in the order of the first planetary gear set PG1, the second planetary gear set PG2, the third planetary gear set PG3, and the fourth planetary gear set PG4 from the engine side.

The input shaft IS an input member, and torque from the engine crankshaft IS input to the input shaft IS after being torque-converted by the torque converter.

The output shaft OS IS an output member that IS disposed on the same axis as the output shaft IS and transmits the changed torque to the drive shaft via a differential device.

The first planetary gear set PG1 is a single pinion planetary gear set, and includes a first sun gear S1, a first planet carrier PC1, and a first ring gear R1, the first planet carrier PC1 supporting first pinions P1 externally engaged with the first sun gear S1, and the first ring gear R1 internally engaged with the first pinions P1. The first sun gear S1 serves as the first rotating element N1, the first planet carrier PC1 serves as the second rotating element N2, and the first ring gear R1 serves as the third rotating element N3.

The second planetary gear set PG2 is a single pinion planetary gear set and includes a second sun gear S2, a second planet carrier PC2, and a second ring gear R2, the second planet carrier PC2 supporting a second pinion P2 externally engaged with the second sun gear S2, and the second ring gear R2 internally engaged with the second pinion P2. The second sun gear S2 serves as the fourth rotating element N4, the second planet carrier PC2 serves as the fifth rotating element N5, and the second ring gear R2 serves as the sixth rotating element N6.

The third planetary gear set PG3 is a single pinion planetary gear set, and includes a third sun gear S3, a third planet carrier PC3, and a third ring gear R3; the third planet carrier PC3 supports a third pinion P3 externally engaged with the third sun gear S3, and the third ring gear R3 is internally engaged with the third pinion P3. The third sun gear S3 serves as a seventh rotary element N7, the third planet carrier PC3 serves as an eighth rotary element N8, and the third ring gear R3 serves as a ninth rotary element N9.

The fourth planetary gear set PG4 is a single pinion planetary gear set, and includes a fourth sun gear S4, a fourth planet carrier PC4, and a fourth ring gear R4; the fourth planet carrier PC4 supports a fourth pinion P4 externally engaged with the fourth sun gear S4, and the fourth ring gear R4 is internally engaged with the fourth pinion P4. The fourth sun gear S4 serves as a tenth rotation element N10, the fourth planet carrier PC4 serves as an eleventh rotation element N11, and the fourth ring gear R4 serves as a twelfth rotation element N12.

In the arrangement of the first planetary gear set PG1, the second planetary gear set PG2, the third planetary gear set PG3, and the fourth planetary gear set PG4, the second rotary element N2 is directly connected with the sixth rotary element N6, the third rotary element N3 is directly connected with the seventh rotary element N7, the fourth rotary element N4 is directly connected with the twelfth rotary element N12, and the ninth rotary element N9 is directly connected with the eleventh rotary element N11, using eight rotation shafts TM1 to TM 8.

The arrangement of the eight rotation shafts TM1 to TM8 is as follows.

The first rotation shaft TM1 is integrally connected with the first rotation element N1 (first sun gear S1), and is selectively connectable with the transmission housing H so as to function as a selective fixing element.

The second rotation shaft TM2 is integrally connected with the second rotation element N2 (first carrier PC1) and is integrally connected with the sixth rotation element N6 (second ring gear R2).

The third rotation shaft TM3 is integrally connected with the third rotation element N3 (first ring gear R1) and with the seventh rotation element N7 (third sun gear S3).

The fourth rotation shaft TM4 IS integrally connected with the fourth rotation element N4 (second sun gear S2), and IS integrally connected with the twelfth rotation element N12 (fourth ring gear R4), and IS directly connected with the input shaft IS, thereby continuously serving as an input element.

The fifth rotation shaft TM5 is integrally connected with the fifth rotation element N5 (second planet carrier PC2), and is selectively connectable with the third rotation shaft TM3 and with the transmission housing H, thereby serving as a selective fixing element.

The sixth rotation shaft TM6 is integrally connected with the eighth rotation member N8 (the third planet carrier PC3), and may be selectively connected with one or both of the first rotation shaft TM1 and the fourth rotation shaft TM 4.

The seventh rotation shaft TM7 is integrally connected with the ninth rotation element N9 (third ring gear R3), and is integrally connected with the eleventh rotation element N11 (fourth planet carrier PC4), and is directly connected with the output shaft OS, thereby continuously serving as an output element.

The eighth rotation shaft TM8 is integrally connected with the tenth rotation element N10 (fourth sun gear S4), and is selectively connectable with the sixth rotation shaft TM6 to serve as a selective fixing element.

These rotation shafts TM1 to TM8 may be selectively interconnected with each other by four clutches C1, C2, C3, and C4 of the control element.

Further, the rotation shafts TM1 to TM8 may be selectively connected with the transmission housing H through two brakes B1 and B2 of the control element.

Six control elements C1 to C4 and B1 to B2 are arranged as follows.

The first clutch C1 is disposed between the fourth rotation shaft TM4 and the sixth rotation shaft TM6, so that the fourth rotation shaft TM4 and the sixth rotation shaft TM6 may be selectively integrated.

The second clutch C2 is disposed between the sixth rotation shaft TM6 and the eighth rotation shaft TM8, so that the sixth rotation shaft TM6 and the eighth rotation shaft TM8 may be selectively integrated.

The third clutch C3 is disposed between the third rotation shaft TM3 and the fifth rotation shaft TM5 such that the third rotation shaft TM3 and the fifth rotation shaft TM5 may be selectively integrated.

The fourth clutch C4 is disposed between the first rotation shaft TM1 and the sixth rotation shaft TM6 such that the first rotation shaft TM1 and the sixth rotation shaft TM6 may be selectively integrated.

The first brake B1 is arranged between the fifth rotation shaft TM5 and the transmission housing H so that the fifth rotation shaft TM5 can function as a selective fixing element.

The second brake B2 is arranged between the first rotation shaft TM1 and the transmission housing H so that the first rotation shaft TM1 can function as a selective fixing element.

These control elements, the first clutch C1, the second clutch C2, the third clutch C3 and the fourth clutch C4, and the first brake B1 and the second brake B2 may be implemented as a multi-plate hydraulic friction device that is frictionally engaged by hydraulic pressure.

As shown in fig. 2, the planetary gear train according to various embodiments of the present invention performs gear shifting by operating three control elements in each gear.

In the first forward speed gear D1, the fourth clutch C4, the first brake B1 and the second brake B2 are operated. Thus, the first rotation shaft TM1 is connected to the sixth rotation shaft TM6 by the operation of the fourth clutch C4. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the fifth rotation shaft TM5 and the first rotation shaft TM1 serve as fixed elements by the operation of the first brake B1 and the second brake B2, so that the first forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and the changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the second forward speed gear D2, the second clutch C2, the fourth clutch C4 and the second brake B2 are operated. Thus, the sixth rotation shaft TM6 is connected to the eighth rotation shaft TM8 by the operation of the second clutch C2, and the first rotation shaft TM1 is connected to the sixth rotation shaft TM6 by the operation of the fourth clutch C4. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the first rotation shaft TM1 serves as a fixed element by the operation of the second brake B2, so that the second forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and the changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the third forward speed gear D3, the second clutch C2, the fourth clutch C4 and the first brake B1 are operated. Thus, the sixth rotation shaft TM6 is connected to the eighth rotation shaft TM8 by the operation of the second clutch C2, and the first rotation shaft TM1 is connected to the sixth rotation shaft TM6 by the operation of the fourth clutch C4. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the fifth rotation shaft TM5 serves as a fixed element by the operation of the first brake B1, so that the third forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and the changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the fourth forward speed gear D4, the second clutch C2, the third clutch C3 and the first brake B1 are operated. Thus, the sixth rotation shaft TM6 is connected to the eighth rotation shaft TM8 by the operation of the second clutch C2, and the third rotation shaft TM3 is connected to the fifth rotation shaft TM5 by the operation of the third clutch C3. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the fifth rotation shaft TM5 serves as a fixed element by the operation of the first brake B1, so that the fourth forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and the changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the fifth forward speed gear D5, the second clutch C2, the third clutch C3 and the second brake B2 are operated. Thus, the sixth rotation shaft TM6 is connected to the eighth rotation shaft TM8 by the operation of the second clutch C2, and the third rotation shaft TM3 is connected to the fifth rotation shaft TM5 by the operation of the third clutch C3. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the first rotation shaft TM1 serves as a fixed element by the operation of the second brake B2, so that a fifth forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and a changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the sixth forward speed gear D6, the first clutch C1, the second clutch C2 and the third clutch C3 are operated. Accordingly, the fourth rotation shaft TM4 is connected to the sixth rotation shaft TM6 by the operation of the first clutch C1, the sixth rotation shaft TM6 is connected to the eighth rotation shaft TM8 by the operation of the second clutch C2, and the third rotation shaft TM3 is connected to the fifth rotation shaft TM5 by the operation of the third clutch C3. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. At this time, the first, second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4 integrally rotate at the same rotation speed as the input shaft IS, thereby implementing a sixth forward speed stage, and the same torque as the input IS output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the seventh forward speed gear D7, the first clutch C1, the third clutch C3 and the second brake B2 are operated. Thus, the fourth rotation shaft TM4 is connected to the sixth rotation shaft TM6 by the operation of the first clutch C1, and the third rotation shaft TM3 is connected to the fifth rotation shaft TM5 by the operation of the third clutch C3. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the first rotation shaft TM1 serves as a fixed element by the operation of the second brake B2, so that the seventh forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and the changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the eighth forward speed gear D8, the first clutch C1, the third clutch C3 and the first brake B1 are operated. Thus, the fourth rotation shaft TM4 is connected to the sixth rotation shaft TM6 by the operation of the first clutch C1, and the third rotation shaft TM3 is connected to the fifth rotation shaft TM5 by the operation of the third clutch C3. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the fifth rotation shaft TM5 serves as a fixed element by the operation of the first brake B1, so that an eighth forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and a changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the ninth forward speed gear D9, the first clutch C1, the first brake B1 and the second brake B2 are operated. Thus, the fourth rotation shaft TM4 is connected to the sixth rotation shaft TM6 by the operation of the first clutch C1. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the fifth rotation shaft TM5 and the first rotation shaft TM1 serve as fixed elements by the operation of the first brake B1 and the second brake B2, so that the ninth forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and the changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In the tenth forward speed gear D10, the first clutch C1, the fourth clutch C4 and the first brake B1 are operated. Thus, the fourth rotation shaft TM4 is connected to the sixth rotation shaft TM6 by the operation of the first clutch C1, and the first rotation shaft TM1 is connected to the sixth rotation shaft TM6 by the operation of the fourth clutch C4. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the fifth rotation shaft TM5 serves as a fixed element by the operation of the first brake B1, so that a tenth forward speed stage is achieved by the cooperative operation of the respective rotation shafts, and a changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

In reverse gear REV, the third clutch C3, the fourth clutch C4 and the second brake B2 are operated. Thus, the third rotation shaft TM3 is connected to the fifth rotation shaft TM5 by the operation of the third clutch C3, and the first rotation shaft TM1 is connected to the sixth rotation shaft TM6 by the operation of the fourth clutch C4. In this state, the torque of the input shaft IS input to the fourth rotation shaft TM 4. In addition, the first rotation shaft TM1 serves as a fixed element by the operation of the second brake B2, so that a reverse gear is achieved by the cooperative operation of the respective rotation shafts, and a changed torque is output via the output shaft OS connected to the seventh rotation shaft TM 7.

As described above, the planetary gear train according to various embodiments of the present invention realizes at least ten forward speed gears and at least one reverse gear, which are formed by operating the four planetary gear sets PG1, PG2, PG3, and PG4 by controlling the four clutches C1, C2, C3, and C4 and the two brakes B1 and B2.

In addition, the planetary gear train according to various embodiments of the present invention substantially improves driving stability by implementing a gear suitable for the engine speed using a multi-gear of the automatic transmission.

Further, the planetary gear train according to the embodiments of the present invention maximizes the driving efficiency of the engine and improves the power transmission performance and fuel consumption using the multi-gear position of the automatic transmission.

The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. The foregoing description is not intended to be exhaustive or to limit the invention to the precise form disclosed, and obviously many modifications and variations are possible in light of the above teaching. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and its practical application to enable others skilled in the art to make and use various exemplary embodiments of the invention and various alternatives and modifications thereof. It is intended that the scope of the invention be defined by the following claims and their equivalents.

Claims

1. A planetary gear train of an automatic transmission for a vehicle, comprising:

an input shaft for receiving torque of an engine;

an output shaft for outputting the changed torque;

a first planetary gear set that is a single pinion planetary gear set and includes a first rotating element, a second rotating element, and a third rotating element;

a second planetary gear set that is a single pinion planetary gear set and includes a fourth rotating element, a fifth rotating element, and a sixth rotating element;

a third planetary gear set that is a single pinion planetary gear set and includes a seventh rotary element, an eighth rotary element, and a ninth rotary element;

a fourth planetary gear set that is a single pinion planetary gear set and includes a tenth rotating element, an eleventh rotating element, and a twelfth rotating element;

a first shaft integrally connected with the first rotating element and selectively connectable with a transmission housing;

a second shaft integrally connected with the second rotating element and integrally connected with the sixth rotating element;

a third shaft integrally connected with the third rotating element and integrally connected with the seventh rotating element;

a fourth shaft integrally connected with the fourth rotating element, integrally connected with the twelfth rotating element, and directly connected with the input shaft;

a fifth shaft integrally connected with the fifth rotating element and selectively connectable with the third shaft and selectively connectable with the transmission housing;

a sixth shaft integrally connected with the eighth rotating element and selectively connectable with at least one of the first shaft and the fourth shaft;

a seventh shaft integrally connected with the ninth rotating element, integrally connected with the eleventh rotating element, and directly connected with the output shaft;

an eighth shaft integrally connected with the tenth rotating element and selectively connectable with the sixth shaft;

a first clutch selectively connecting the fourth shaft and the sixth shaft;

a second clutch selectively connecting the sixth shaft and the eighth shaft;

a third clutch selectively connecting the third shaft and the fifth shaft;

a fourth clutch selectively connecting the first shaft and the sixth shaft;

a first brake selectively connecting the fifth shaft and the transmission housing;

a second brake selectively connecting the first shaft and the transmission housing;

the first planetary gear set includes: a first sun gear as a first rotating element, a first planet carrier as a second rotating element, and a first ring gear as a third rotating element;

the second planetary gear set includes: a second sun gear as a fourth rotating element, a second carrier as a fifth rotating element, and a second ring gear as a sixth rotating element;

the third planetary gear set includes: a third sun gear as a seventh rotating element, a third carrier as an eighth rotating element, and a third ring gear as a ninth rotating element;

the fourth planetary gear set includes: a fourth sun gear as a tenth rotating element, a fourth carrier as an eleventh rotating element, and a fourth ring gear as a twelfth rotating element.

2. The planetary gear train of an automatic transmission for a vehicle according to claim 1, wherein the gear realized by the selective operation of three control elements of six control elements including four clutches and two brakes includes:

a first forward speed stage formed by operations of the fourth clutch, the first brake, and the second brake;

a second forward speed stage formed by operations of the second clutch, the fourth clutch, and the second brake;

a third forward speed stage formed by operations of the second clutch, the fourth clutch, and the first brake;

a fourth forward speed stage formed by operations of the second clutch, the third clutch, and the first brake;

a fifth forward speed stage formed by operations of the second clutch, the third clutch, and the second brake;

a sixth forward speed stage formed by operations of the first clutch, the second clutch, and the third clutch;

a seventh forward speed stage formed by operations of the first clutch, the third clutch, and the second brake;

an eighth forward speed stage formed by operations of the first clutch, the third clutch, and the first brake;

a ninth forward speed stage formed by operations of the first clutch, the first brake, and the second brake;

a tenth forward speed stage formed by operations of the first clutch, the fourth clutch, and the first brake;

a reverse gear formed by operations of the third clutch, the fourth clutch, and the second brake.

3. A planetary gear train of an automatic transmission for a vehicle, comprising:

an input shaft for receiving torque of an engine;

an output shaft for outputting the changed torque;

a first planetary gear set as a single pinion planetary gear set and including a first sun gear, a first planet carrier, and a first ring gear;

a second planetary gear set which is a single pinion planetary gear set and includes a second sun gear, a second carrier, and a second ring gear;

a third planetary gear set as a single pinion planetary gear set and including a third sun gear, a third planet carrier, and a third ring gear;

a fourth planetary gear set which is a single pinion planetary gear set and includes a fourth sun gear, a fourth planet carrier, and a fourth ring gear;

a first shaft integrally connected with the first sun gear and selectively connectable with the transmission housing;

a second shaft integrally connected with the first carrier and integrally connected with the second ring gear;

a third shaft integrally connected with the first ring gear and integrally connected with the third sun gear;

a fourth shaft integrally connected with the second sun gear, integrally connected with the fourth ring gear, and directly connected with the input shaft;

a fifth shaft integrally connected with the second carrier and selectively connectable with the third shaft and selectively connectable with the transmission housing;

a sixth shaft integrally connected with the third carrier and selectively connectable with at least one of the first shaft and the fourth shaft;

a seventh shaft integrally connected with the third ring gear, integrally connected with the fourth carrier, and directly connected with the output shaft;

an eighth shaft integrally connected with the fourth sun gear and selectively connectable with the sixth shaft;

six control elements selectively interconnect the shafts or selectively interconnect the shafts with the transmission housing.

4. The planetary gear train of an automatic transmission for a vehicle according to claim 3, wherein the six control elements include:

a first clutch selectively connecting the fourth shaft and the sixth shaft;

a second clutch selectively connecting the sixth shaft and the eighth shaft;

a third clutch selectively connecting the third shaft and the fifth shaft;

a fourth clutch selectively connecting the first shaft and the sixth shaft;

a second brake selectively connects the first shaft and the transmission housing.

5. The planetary gear train of an automatic transmission for a vehicle according to claim 4, wherein the gear stage realized by selective operation of three control elements of the six control elements includes: